Rotary fluid displacement mechanism



March 2, 1954 AAAAAA AAAAAAAAAAAAAAAAAAAAAAAA SM March 1954 H. A. GRAHAM ROTARY FLUID DISPLACEMEN'I: MECHANISM 10 Sheets-Sheet 2 Filed Feb. 20, 1952 Army/.. V

March 2, 1954 A. GRAHAM ROTARY FLUID DISPLACEMENT MECHANISM Filed Feb. 20, 1952 10 Sheets-Sheet 3 INVENTOR. ARC/.D A. GMMM Filed Feb. 20, 1952 March 2, 1954 GRAHAM 2,670,688

RY LUID DISPLACEMENT MECHANISM 10 Sheets-Sheet 4 VENTOR.

IN HAROLD ,4. ami/A March 2, 1954 Filed Feb. 20, 1952 H. A. GRAHAM ROTARY FLUID DISPLACEMENT MECHANISM 10 Sheets-Sheet 5 INVENTOR. l/AQOLD A. GBW/AM March 2, 1954 GRAHAM 2,670,688

ROTARY FLUID DISPLACEMENT MECHANISM Filed Feb. 20, 1952 10 Sheets-Sheet 6 II 'II Q INVENTOR. ll/LQOLD A. GP/MAJ March 2, 1954 GRAHAM 2,670,688

ROTARY FLUID DISPLACEMENT MECHANISM Filed Feb. 20, 1952 10 Sheets-Sheet 7 k INVENT HABOLD A. GRAH wa @iz/22 March 2, 1954 GRAHAM 2,670,688

ROTARY FLUID DISPLACEMENT MECHANISM Filed Feb. 20, 1952 lO Sheets-Sheet 8 INVENTOR. MROLD A. GQ/If/M 7 March 2,1954

Patented Mar. 2, 1954 ROTARY FLUID DISPLACEMENT MECHANISM Harold A. Graham, Parma Heights, Ohio Application February 20, 1952, Seral No. 272,681

The present invention relates to a novel mechanism for use in rotary devices wherein fluid is either moved by the device or the fluid serves as a movant for the rotary mechanism. The nature of the invention is such, therefore, that it may be adapted for use as a fluid pump, a fluid motor and, with suitable fuel feed and ignition means, may serve also as an internal combustion engine.

In generalized terms, a structure embodying this invention operates on what herein is termed a mobile seal relay or exchange principle, by the provision of a plurality of relatively displaceable orbitally mobile seals between, for example, the outer and inner peripheries of two' suitably contoured relatively rotatable surfaces-such as a rotor and casing-constituting walls of a fluid chamber. The mobile seals divide the fluid chamber into a plurality of smaller fluid chambers which Vary in size under operatively varying conditions of relative seal positions as the rotor is turned. E'ach seal alternates in function as a stationary wall and as a moving wall in an individual fluid chamber of varying volume. The application of the principle of this 'invention will hereinafter be disclosed in various structural forms for use in pumps, fluid driven motors and internal combustion engines.

An Object of the present invention is to provide a rotary mechanism of the character described wherein movable seals between two relatively rotatable parts provide a plurality of fluid chambers of operatively varying size.

Another Object of the invention is to provide a mechanism for use in rotary fluid `pumps, motors or like devices wherein which may be self-compensating for wear in the device.

Another Object of the invention is to provide a mechanism for use in pumps, motors or engines wherein critical toleranees are generally avoided in machining the working parts.

Another object is to provide a rotary mechanism of the character described wherein the seals between the relatively movable'parts increase in effectiveness as the fluid pressures handled therein increase in magnitude.

Another Object is to provide a rotary positive fluid displacement device which is capable 'of handling large fluid volumes at relatively high pressures. l y

With the above and other objects in 'view, which will be apparent from the detailed description which follows, the invention consists in certain novel features of construction andcombination of parts which will be readily understood seals are provided 17 Clams. (01. 103-129) by those skilled in the art to which the invention appertains. In the drawings which illustrate an embodiment of the invention- Fig. 1 is a cross section through a pum constructed according to the invention wherein rollers provide mobile seals, the section being taken perpendicularly to the aXis of rotation along the line I-l of Fig. 2;

Fig. 2 is a sectional view taken along the line 2-2 of Fig. 1;

Fig. 3 is a fragmentary view taken along the line 3-3 of Fig. 2 to show in detail an inlet port of the device;

Fig. 4 is a schematic representation of the invention as realized with another form of casing and rotor;

Fig. 5 is a fragmentary view showing another fluid port arrangement in a device of the general form shown in Fig. 4;

Fig. 6 is a fragmentary schematic view showing a form of'the invention wherein the casing is rotated; v

Fig. 7 is a schematic representation showing the mechanism and principles of this invention adapted to an internal combustion engine;

Fig. 8 shows the invention embodied in a pump using roller seals with another rotor and race contour and port disposition, the representation being a section perpendicular to the axis;

Fig. 9 is a section taken at e 9 of Fig. 8;

Fig. 10 is a cross section taken perpendicularly to the axis of a pump wherein is used another form of mobile seal in the form of a sliding block or piston;

Fig. 11 is a section taken at ll-ll in Fig. 10;

Fig. 12 is a fragmentary detail view -of the spindle or carrier of Fig. 10;

Fig. 13 is a detail of the outer race of Fig. 8;

.Fig. 14 is a detail of a sliding seal of Fig. 10;

Fig. l la shows in detail sealing bars which may be used with a sliding block or piston such as shown in Fig. 14;

`Fig. 15a, b, c, d, e shows various types' of locking means which may be used with the type of seal shown in Fig. 10;

Fig. 16 is a schematic representation similar to Fig. 7, but utilizes the sliding block type of mobile seal; V

Fig. 17 is another form of roller seal retaining formation for the outer race Fig. 18 is a vertical longitudinal section of a device utilizing a third form of seal and seal exchange structure;

Fig. 19 is a section taken along .the line l9-l9 of Fig. 18 but with certain rotatable parts displaced from the positions of Fig. 18; and

Fig. 20 is a fragmentary circumferential section taken along the line 20-28 of Fig. 18.

Thus, Figs. 1-9 show devices utilizing mobile seals of the roller type, while Figs. -16 relate to devices employing the sliding block type seal.

In Figs. 1, 2 and 3, there is shown a pump constructed according to this invention which includes a pump casing generally indicated lil, a pump shaft |I on which there is mounted a spindle or rotor element [2, and right cylindrical roller elements laa, l3b, i3c, i3d and l3e which are interposed between the rotor and casing. The roller elements may be hollow or solid. As here shown, the casing e comprises a hollow casing midsection having a suitably contoured inner roller race surface s on which the rollers run, as hereinater described, and two casing end plates H and la. A liquid gasketing compound may be applied to abutting -surfaces to seal the casing elements, or gaskets may be used. The casing may, of course, be fanned in any way to include the operative elements as hereinater described. Suitable shaft bearings [3 and are provided in the pump `cover plates i'l and i respectively, the outer races being retained in position by expanding snap rings 22. These bearings may be of the "floating" type, in which case there is provided for each a ring of resilient material 2] between the bearing and the cover plate, the cover plate then being recessed at 23 to allow clearance for the inner bearing race. When floating bearings are used, then suitable shait clearance should be present at the shaft apertures in cover plates 11 and is and pressure plates 32 and '33.

Inlet and outlet ports 24-,-24a and z5 2sa open inwardly through the casing to the roller operating space provided between' the rotor 12 and the race surface is, these ports communicating respectively with an annular inlet manifoldZB and annular outlet manifold 21 in the casing. The inlet manifold 25 is shown formed by matching annular channels `provided in the cover plate 18 and the corresponding face of the midsection i. The outlet manifold similarly is an annular channel formed in the midsection 15. Inlet and outlet piping connections 28 and 29, here shown threaded, are provided on the casing opening into the manifolds.

v The rotor 2 is provided with three roller carriers 30 having forward faces or impelling shoulders 30a, 301), 380 and rear surfaces 30'a, 30'17, and 30'c. The shoulders serve to move rollers [3 about in the pumping chamber constituted by the race wall 16, the rotor l2 and the pressure plates 32 and 33. These pressure plates have a beveled periphery generally conformed in shape tothe race face IS and are fitted into each end of the midsection 15 to provide side walls for the pumping chamber. Packing 34 and 35 for sealing the beveled periphery oi each side plate 32 and 33 against the race face is is held in position by the respective cover plates. l

- As is seen more clearly in Fig. 2, the inner face of the cover plates are recessed at 36 and 31 to provide a slight clearance between the respective end plates near the outer periphery thereof, .while the cover plates have deeper annular recesses 38 and 39 concentric to the shaft holes. o-ring seals 40 'and 41 on the she-ft li are disposed' in recesses peripheral to the cover plate shaft holes, to form rotary seals between the rotor shait H and corresponding pressure plates and cover plates.

The annular walls 42 and 43 of these o-ring recesses preferably extend beyond the center of the o-rings.

The inner face of each pressure plate may have a shallow circular recess 44 concentric to the shaft hole thereof to provide a chamber between each end of the rotor and the corresponding pressure plate. Vent channels 45 extend from these recesses M through the pressure plates to the chambers formed between the cover plates, pressure plates and the O-ring seals, which latter chambers in turn are in communication with the annular outlet manifold through Vent channels in the pump casing, that is, through vent channel 48 from recess 38, and through channels 48 and 49 from recess 38. The side or pressure plates 32 and 33 are also provided with additional Vent holes 50 near the port in the casing, the location of which is hereinafter described, so that the outer ends thereof open to the shallow recesses 36 and 31 and hence are in communication with the chambers between the pressure plates and cover plates. Though vents represented by dotted lines in Fig. 2 would not strictly be shown in Fig. 2 with the section taken along line 2-2, they are dotted in to show more clearly the intercommunication of the Vent system. The function and purposes of these several Vents will be later described relative to the operation of the pump.

Fig. 1 shows one manner of shaping rotor 12 and roller track or race IS when two roller exchange stations and three carriers are used. Five rollers are provided-one for sealing each exchange tation and one for each carrier on the rotor. On opposite sides of each station inlet and outlet ports 24 and 25, Na and 25a 'opento the track face. In Fig. 3, a detail of the track face about an inlet 'port 24 but typical oi the other port openings, the port is shown as having a shorter length than the rollers, so that the roller will have some continuous bearing surace in passing the port Opening. Hence the midportion [5 of the casing should be of sufcient thickness to accommodate the length of the roller cylinders and the two pressure plates. Generally the dimensioning of the port openings is a compromise between demands of flow capacity and sealing function for a given gross pump size. Hence, usually a rectangular port Opening is used, disposed lengthwise to the track Width to minimize leakage as a roller passes the Opening.

In the situation shown by Fig. 1 the following operative conditions prevail: The rotor l2, with its three roller Carriers 30 disposed in threefold symmetry about the shaft axis, is carrying rollers Isa, 130, i3d in a counter-clockwise direction, while roller-s ae and |3c form seals between the rotor surface and the track is behind the inlet ports 24a, and 24 respectively. The roller I3a, as it is carried away from inlet port Mo, draws fiuid into the expanding chamber extendin between i3a and the comparatively stationary seal i3e. Simultaneously 130. is expelling, through outlet port 2-5, the fluid in the contracting chamber between |3a and the substantially stationary seal l3b, and the pressure developed thereby holds l3b in seaiing contact with the radially inward siopes on the track surface is and the rear 'carrier surface 30'b. Roller l3c, which shortly beforewas in the present position of l3b, has 'been displaced (by an action Similar to that occurring between |3d and l3e) and has been picked -up .by carrier face 3017. Thus as `i3c is carried forward it also creates-an expanding chamber with |3b for the influx of fluid through port 24, and a chamber with I 3d from which fluid is expelled through outlet port a as 130 advances. The rollers |3d and |3e are in-the relay or exchange process as the corresponding seal carrier and retaining formations transit each other. Roller l3d, still in driven contact with the edge of carrier face '300, has already come into proximity with |3e and fluid pressure therebetween is eifecting a displaceme'nt of the latter up the forward slopes from the exchange station which is permitted by the radially receding curve of the rear carrier surface to'a. The fluid pressure developed between |3d and |3e serves also as a cushion keeping the rollers from tapping in the exchange process thereby furthering noiseless operation.

It may here be noted that there is a space of fluid not in direct communication with inlet or outlet ports 2411 and 241) between the race is, the pressure plates 32 and 33 and rollers lsd and l3c, and between the press-ure plates, the rollers |3d and 136, the rear carrier surface 3'a and the forward carrier face :2. 'Since this space varies in volume, suitably placed vents are provided to prevent difiiculties in the roller exchange process because of trapped fluid, particularly when relatively incompressible liquids such as eils are handled. To this end, the aforernentioned vents are provi-ded through the pressure plates, and also the vents 53 at the bottom of each carrier forward face, which each open into channels 54 extending lengthwise of the rotor 12. The ends of each channel 54 opento the circular recesses 44 thus providing venting at any position of the rotor. Thus through the series of recesses or vent channels, as the case may be, 53, 54, 44, 45 and through 50, venting for the trapped liquid spaces is provided to the two chambers behind the pressure plates formed by recesses 38 and 39 in the cover plates. These chambers are vented to the high pressure outlet manifold as already described, through vent 45 or through vent 48-49, so tha-t a suflicient back pressure is maintained at the exchange stations to provide a fluid cushion between exchanging rollers.

These Systems of venting channels also have the further function of supplying fluid pressure to the outer faces of the pressure plates to produce endwise pressure, additional to that of the compressed O-ring seals, for maintaining the seal of the pressure -platcs on the ends of the rotor and of the roller cylinders, The recesses 44, by providing a clearance between rotor and pressure plates over the central area where wear is less rapid, also allow the pressure plates to "feed" inwardly to compensate for wear. various positions and interconnections of the vent channels may of course be used depending upon the fluid handled, the metal distribution in the casing, and the shape of rotor 42 and race s.

In view of the above described operation, an analysis of rotor and roller track shapes may now be more clearly understcod. The fact that the rollers function as mobile seals between rotor and. track indicates that curved portions of the roller contact surfaces should be cylindric surfaces, the genetrices of which are parallel to each other and to the axis of the rotor. Here the term cylindric is .used in the general geometric sense, not necessarily signifying circularly cylindric. Flat portions of the roller contact surfaces would be similarly generated Hence the contacts of each roller with the' rotor and track surfaces are parallel and, theoretioally, line contacts.

The forward face of each carrier, which may be flat, preferably has a backward slope that the roller may move more readily outward in traversing radially outwardly receding portions of the race and thereby maintain the seal. Thus as a roller is advancing, centrifugal force urges the roller outwardly against the race and also the reaction force or back pressure of the fluid being moved wedges the roller .between rearwardly converging surface portions of the carrier and the race until the roller' escapes the forward carrier face at an exchange station, as is about to occur in the situation of |3d in Fig. 1. To allow such escape,'the space between the radial extreme of the carrier and the race must be sufficient to accom-modate the roller at the escape point of the exchange station. This is of course a general requirement for similar mechanisms. r

The forward part of the exchange station slopes inwardly toward the rotor so that rotor and race provide forwardly convergent surface portions in which a roller .may wedge to form a seal as is formed by roller I3b. 'As a roller is displaced forwardly to escape the exchange station, it must move inwardly relative to the rotor, for which' suitable clearance between race and carrier surfaces must be provided. The inlet and outlet :ports are so located that between any successive 'p'air, comprising an inlet and an outlet, there is provided at all times at least one roller forming a positive seal.

In Fig. 4 there is shown schematically another form of the invention in which the rotor member and outer race member are of generally concentric form. The rotor 10 is providedwith four carrier grooves 'IZa-b-c-d spaced equally about the inner* periphery thereof, while the casing 'H has three equally spaced exchange station grooves 13a-b--c. Each groove is of symmetric form, the length of each being dimensioned so that no more than one roller seal may be completely accommodated in each. The shoulders or ends of each groove are sloped to provide wedging action on the seals. The depths of the grooves are dimensioned with respect to theconcentric surfaces and the roller diameters so that when the seals are held against the shoulders of the grooves of one member they bear on the concentric surface of the other member. To facilitate escape of rollers from grooves, the shape and height of the shoulders should be such that the line of contact of roller when held against the shoulder is -at a height from the gr'oove bottom less than the height of the roller axis from'the bottom-that is, the lower the line of-ccntact of shoulder on the roller toward the groove bottom, the more easy the escape during exchange and the stronger the wedging force developing sealing pressure at other times.

About each exchange station 13 a pair of ports 15 and 16 Opening through the race face is provided symmetrically disposed with respect to the groove and spaced so that at all times rollers translated by the rotor form seals therebetween. With the symmetrical disposition of the grooves on the respective members, the symmetric form of the grooves and symmetric disposition of the fluid ports about each exchange station groove, the pump is reversible as to direction of flow by simple reversal of the direction of rotation.

As shown in the figure with the spindle rotating clockwise, the pairof rollers 'Ma and 'mb at the exchange'station 13a are about to 'enter the exchange process. The space between the rollers contains compressed fluid since the seal Na has passed the port 15 serving as an exhaust port. When this form of pump is used for compressible fiuids such as air and other gases no vents need be provided and the fluid compressed in the space serves as a cushion to prevent tapping of the rollers and to aid the exchange process. The roller 140, as it is carried ahead away from the station 'laa, is drawing fluid into the expanding space bounded by "c and 'Mh through the port 'Isa from a suitably placed manifold in the casing, while the fiuid in front of the roller 'Me is being carried forward and expelled through the port 'lb, The roller "d lodged against the for- Ward incline shoulder of the groove 131) provides the seal for the contracting chamber formed with the roller 'He to cause the expulsion of the fluid through the port 1th. The operation in general is Similar to that carried on in the pump of Fig. 1.

In Fig. 5 there is presented a. fragmentary view showing another arrangement of the ports with respect to the exchange station, the casing 80, rotor 8! and grooves 82-83 being similar in form to those of Fig. 4, but the exhaust port 85 opens into the bottom face of the exchange or outer race groove 83. With this manner of the disposition of the ports the device is not reversible. The groove 82 on the rotor is carrying the seal 83a in a counter-cloekwise direction, thereby drawing liquid through the inlet port 85 into the expandin chamber formed in conjunction with the seal 842). At the same time another roller (not shown), being carried forward toward the station 83 by another groove on the carrier, forms 'with roller adb-a contracting chamber expelling liquid through the exhaust port 86. The main requirement for the positioning of the port 86 is that it be behind the sealing position of the roller 841) to allow unimpeded flow of the exhausted fluid.

As the form of the ports and manifolds in Figs. i and 5 may be Similar to that of Figs. 1-3, these are not described nor iilustrated in detail. Venting systems may be provided as needed, and end plates and end covers of suitable form, e. g. corresponding to those of Fig. 2, may be used. Moreover, in all the foregoing forrns, if desired, side pressure plates may be omitted, especially where the pump will not be operated at low speeds, or where leakage is not important, and then cover plates with a close roller end clearance provide the end walls of the fluid working space. Furthernore, in place of pressure plates forming the side walls of the fiuid working space, the casing side walls may serve this purpose as in the casing form of Fig. 11 hereinafter described. In such a case, if desired to seal rotor to casing more effectively, a sealing ring may be provided in a groove cut into each casing wall with underlying resilient means to urge the ring toward the side of the rotor.

In Fig. 6 there is shown schematically by a fragmentary view a form of the invention wherein the casing or outer race 99 has gear teeth 9! formed on its outer periphery whereby the casing is driven by a pinion 92, while a central member corresponding in form to the rotor of the previous forms is held stationary. In this case the inlet and outlet ports 98-91 are provided on the stationary central member 94. The exchange station grcove 95 on stationary member 94 has the inlet part 96 Opening through its rear slope. while the outiet port 91 opens to the race face of the stationary member slghtly forward of the exchange station. The exchange station groove 95, carrier groove 98 and the stationary and moving race faces are Similar in form to the corresponding parts of Figs. 4 and 5, and the relay or exchange action, sealing and pumping action of the roller seals 98 and [00 are analogous to that already described. With this disposition of the -ports a single exchange station may be used on the stationary member 94 with one or more carrier grocves in member 80. A plurality of exchange stations may be used, in which event there must be an equal or greater number of carrier grooves with one roller seal provided for each groove on the two members. The casing and central member, of course, would be modified as known to the art, to extend one end of the central member through one end of the casing with a rotary seal therebetween, in order to allow external connections to the inlet and outlet ports.

Thus far the embodiments of this invention have been described as fluid pumps. However, with suitable port and roller groove arrangements, a fiuid actuated motor may be had. For example, assuming the structure Similar to Fig. 5 to have but a single groove on the casing, a diametric pair of grooves on the rotor, and the port 86 to be supplied with fiuid under pressure and port used as an exhaust port, the rotor 8! would be turned clockwise by fiuid pressure acting between stationary seal 841) and moving seals bearing against the clockwise shoulders of grooves on the spindle or rotor. Fluid would exhaust freely through port 85, now serving as an exhaust port. The location of the ports and the dimensions of the seals, grooves, inner and outer race diameters would of course, as in the pumps, be selected so that at least one of the roller seals maintains a seal between the fluid inlet and outlet ports as long as possible to minimize leakage. Where a plurality of exchange stations is provided and there being at least one more carrier groove than exchange stations (as in Fig. 4) a fiuid motor with the port arrangement of Fig. 5 would have a positive seal between adjacent inlet and outlet ports at all times.

An internal combustion engine is shown schematically in Fig. '7 utilizing the exchanging seal principle hereinbefore discussed with respect to fluid pumps and motors. The casing o and rotor H I are provided with coaxial race surfaces having each four equally spaced exchange grooves, the exchange grooves I i3c-b-c-d and carrier grooves Ha-b-c-d while eight roller type seals are used, one for each groove. Thus with each quarter turn of the rotor four seal exchanges occur simultaneously. The remaining parts are described to correspond to the clockwise driving of the engine as shown in the drawings. Each outer race groove of one diametrically opposite pair, 317 and l l3d, is provided near its clockwise edge with a simple firing device comprising an insulated conductor ll'l extending through the casing and held flush with the race face by a threaded bushing us threaded into the casing. By grounding the casing to one side of an ignition circuit and connecting the ignition wire I s to the other side of such circuit. means is provided for firing a combustible fuel mixture compressed, for example, between rollers H5c and nd. The specific ignition system is not described in detail, since a variety known to the art can be utilized. However, a low voltage source could abe used, for as a roller passes over and leaves the end of the igniter conductor [1, a spark is produced suitable for igm'ting the combustible mixture. About each of the other diametrcally opposite pair of exchange 'grooves [[3a and I3c, exhaust outlets l2l, fuel mixture inlets [23, lubricant injecting channels [24 and lubricant injecticn pressure ta [25 are disposed. Each fuel inlet l2l, which is connected to a fuel mixture injection or carburetion system, opens to the casing race surface on the clockwise side of the corresponding exchange groove, and eachexhaust outlet [2I enters the bottom of its groove at a position providing a, sealing surface between the exhaust outlet and the fuel mixture inlet against which a roller seal may abut. I-,Ience, for example at [[3a, when roller [l5a is seated to form a seal against the forward or clockwise edge of the groove, an expanding cha-mber is formed in conjunction with roller [[sb being advanced by the rotor. Since this chamber is sealed from the exhaust ports, fuel mixture is drawn thereinto from inlet [23 as roller H5b advances. As shown in Fig. 7, at one pair of exchange stations I3b and ll3d) the forward seals [5d and |5b have been carried by the rotor beyond the ignition point. The fuel compressed between roller pairs lc-l [5d and [[5g-l [572 has been ignited and, in expanding against the forward seals [[5d and [[Bg, is driving the rotor in a clockwise direction. Combustion products from a preceding ignition are being expelled through exhaust ports 21 by the rollers l 511 and I [572 as they are advanced by the rotor. Forward of the other pair of exchange stations the advancing rollers [[5b and I [5,f, which have passed beyond the fuel inlet, are drawing in fuel mixture behind them. As these latter seals advance, fuel mixture taken in during the preceding quarter turn of the rotor is being compressed in the spaces between roller pairs [5b-ll5c and llf-Ilg preparatory to the firing which will occur after the rollers in each of these pairs exchange position.

By means of the channels [24 oil from a suitable reservoir may be injected in measured amounts into the space between rotor and casing to lubricate the moving parts. The periodic pressure differential developed between channel [24 and pressure tap [25 as rollers traverse the inter- -vening space may be used to inject the oil or to actuate an oil injection and -measuring device. Since the specific oil feed mechanism is not as such part of this invention it is not shown.

A controlled exhaust port, having a spring biased valve member, for example, may be used to control the exhaust pressure for the maintenance of a compressed gas cushion between rollers exchanging at the exhaust station for the avoidance of roller tapping when necessary.

In Figs. 8 and 9 there is shown a device having another form of casing and of exchangestation -and rotor carriercontour. The casing as shown .in Fig. 9 comprises the two side plates [30 and [32, and. the annularshell [3I therebetween held together by means of bolts [33. The rotor [35, with cylindrical periphery coaxially disposed with respect to the generally cylindrical inner race face of the casing, is keyed to a shaft [34 journalled in the bearings [36, [3] in the casing side plates. Between th'eplate [32 and the bearing [36 an 0-ring 133 may be provided in plate recess l39to form a rotary seal between shaft and casing. The axial length of the annular portion of the casing is greater than'the axial length of the rotor to accommodate thrust spring [42 and the composite pressure plate comprised of disks [40 and [4[ held together by screws [51. The outer edge of disk Mo is beveled to accommodate the packing ring [43 which is forced outwardly by the pressure of the second disk (controlled by screws 'i) to form a peripheral seal to the casing. The bearing structure or manner of keying rotor to shaft allows some axial displacement of the rotor whereby spring pressure urges the pressure plate against one face of the rotor and the other face of the rotor against the casing plate [30. The inner portion of each rotor face may be recessed around the shaft similarly to the rotor of Fig. 1 for more even wearing. As shown in Fig. 8, for a clockwise rotating rotor, the exchange station on the casing comprises a recess [55 and a projection, here in the form of a cylindrical pin [5,4 with axis parallel to the axis of the rotor and with a portion of its cylindrical surface projecting out of the cylindrical face of the outer race. With the periphery of the composite pressure plate recessed and the packing Ma shaped to accommodate the pin [54, rotation of the pressure plate is pre- Vented. The inlet port [48 opens to the threaded inlet in the casing. The outlet port [49, disposed somewhat clockwise beyond the pin in the pressure plate, opens through the space between the pressure plate and the casing to the threaded outlet [53 in the plate [32. The generally cylindrical rotor face has two diametrcally disposed carrier structures, each similar in form to the exchange station, comprising pins [52 and recesses [53. Three roller type seals [44, [45, [46 are provided, one for each groove, whereby there is always provided one roller at the exchange station, held from translation by the pin [54 and forming a seal between the casing and the cylindrical rotor face, and two roller seals being advanced by coresponding pins on the rotor.

Thus, one seal [44, as it is carried away from the exchange station by the rotor, draws in fluid behind it through the intake port [48, while the second advancing seal [45, diametrcally opposite, is expelling liquid through the outlet port, while fluid taken into the space between the two moving seals during the previous half turn of the rotor is being carried toward the exhaust port. As shown in Fig. 8 a carrier brings a moving seal [45 into the exchange station, the roller end cuts off the outlet port me and develops a body of compressed fluid between it and the stationary seal, which forces the latter forward over the pin i54 toward the recess in the rotor as the ad- Vancing seal [45, acted on by centrifugal force and fluid pressure, escape over the rotor pin into the exchange recess. The function of the two seals then become reversed, as is usual in the devices thus far described, the seal which has escaped from the rotor moving forward against the casing pin to form a stationary seal, while the second roller moves backwards against the rotor pin to form a moving seal with the casing. With a pump of this type moving at relatvely high speeds, close fitting of the rotor ends and roller sealer ends is not required. As pressure is developed by the pump, a corresponding thrust force is developed on -the pressure plate to maintain the end sealing for the fluid working space 'of the pump. Where non-compressible fiuids are to be handled, a venting system may be providedas already described for other devices 'at the exchange station. However, with compressible fluids, such as gases, this is usually unnecessary and in either event the compressed fluid between `second form of .mobi

ca ier g ooves ni,

king space 'throg hfthe side .152 aga positin somewhat eloknis'e :beyond the rooveagainstga -shoulderthereof to look the -b1oclg-at the ,exchange;station. A .a ;The effective: length of v the -grpoves suchithat (whena pair of ,sliding pi tons come intokadjacent relation ,ors exchange, `rollers ;from both, blocks qannotbe fully accommodated in a `,single groove.

asone 'block, With its vrollers pressed .downzwardlytolock-it at a carrier groove of the rfotor, =garried ,into :.an exchange station,.. .the b1 ock looked at thenexchange' station by. anontwardly proieetingnroner inthe exchangezstation groove is urged forward ,either .by physical :contact or thx.. pressure of ,compressed x fiuid, whereby. its rgllereare cammed inwardly by the sloping; forward ,eghange groove shoider toward the: oryard end pi 'the carrier groove At the same ilm th xl f .t e t o k are b n camgpedypwarqlly a w i l on h p n -rea ;face ofjthe carrier grooVe toward the year end of ;th n ,han sta qnx rooye ,As-theseicamm-n movements of the rollers are completed, the inner a e; clar path during the exchange ibhr the rarw'ra 'b-qck sapqs he grboveg mo ir g t e oter roermto vtrjee grqoy'e tpo the'blook against dispIaoem P-V while the enter rouer pithe :forward waongee p'es bv'e'r the mwera fshoulder 'of the exch nge e it'sjinner .roiler i` to the'tder'- ,to look the *forward b q' to the r'oilerp'air has been 'de- 'Sor'ibed asfmoi ng munn 'in the *slot I m *in 'se uefn'ce of 'a amming action, it isfto 'be noted that during the fexohan'g 'process, 'the ;messa e of fluid oonres'sedtherehetween also acts to dis- *paee 'the rollersfradially for release 'of the blocks, even when 'the latter do notqite *come into'c ntact. Hence, athoghthe manner of lookng'the mobfle seals tocarrier or casing 'is somewha different from 'the 'mechan'sm s using rol'ler "seals, the net result is the same inasmch 'as an "e'x`- chage of mobile seals is efiected. V A Figs. 12 'a 'd 13 'are 'fragmen'tary siiews showing details, of the construction 'of the i'dt'or [65 ana yiindriai `s`he1`1 |'B`3 rescti ely, While 1'4 and l ta respectiifely show'detals of the contriiovtionofbre of the vsllidin g bloqltype sals it's ga 05: sea"ng. neans tab, 'which may bede'sirable 'in some jservice conditions f; semg :the hlqok 'h ld b cr w riengrooves, as ;l '[Lpnt into-the periphery before assembly "of :the rotor. The 'block 168 may,be *formed ;of end. members, l-84,;be w w i h gby cr wse 8 ,a e eld .c t r membe s! 5 'm e relation to each other to form the roller slot j 19. ros th ej endia e ;a d :th inner nd-e u vesiu es oi h b ka t-r spectiveythe radial and transverseslots la? and [8,8 of :ectangu1ar ;cross section. Disposed.. in eachof these-slots, as; shown more' clearly; in.;Fig. l da, sis-;a sealing :bar: 1190 biased outwardly'by the undulantspringmember, I-BI. With the structure .above desori'bed the width of --the grooves issuffeient toxaccommodate the'glength of the rolle'rs but does note-extendthe full axial vthickness of ::the hlocks, sogthatentirely around both rotor and ;casing race :facesthere is' provided a continuous bearing surfae'e :for :the sealing bars I-Q postione'd ,transversely across theficurved inner and outernfaces :of thexpiston blocks. 'Grooves of othercircumferential contourmay be used proyded the a'carrier 'and ::exchange grooves :are :shaped to :allow the simultaneous oppositeiytdirected movements of' the' looking devi'ces: in-:an: exchangingpair of bl'ocks. In'the ump lof Figs. -10-1-1 thevsea1ingbars 190 maybe* omitted:n .the :slidin'g 'piston ;type .seals I'BB where :the service requirements ;of the 'ipump do 'not demand so -positive-a-sealin'g..

, In:Fig.j 15 several forms` of loekingdevices'for the-sliding blockty pe's'eals arediselose'd. Thus mg. "a ish'ows a: bairof rolle'ns* such as 'is :used in Figs o to u; l:5b. .trip1e-ti'ered:rollers; .1 503 tahular shaped" pin `'With 'seii-rcylindrieai ends. l''d. :a nylindrical :pin with hemisphericai ends, `'and l e as a -of ball bearngs. With' thloki components l5a-c inclusive, carrier and spindle rooves of the general form of those shown in Figs. 12 and 13 would be used, while with looking components of the form of I d or |5e the grooves preferably would be in the form of channels having Semi-circular cross Sections, while slot |l0 would be replaced by a cylindrical bore. With seals of the piston or sliding block type used in place of roller seals, the inlet and outlet ports would be positioned on the casing at distances suflicient to ac-commodate the length of the slidng blocks. The variations in numbers of exchange stations, carrier grooves, use or non-use of venting Systems or end sealing means for the fluid operating chamber may be such as those already described for the devices embodying roller type seals and, as previously discussed, 'by proper disposition of the ports a reversible pump or a fluid driven motor may be had.

In Fig. 16 there is represented schematically an internal combustion engine usin seals of the sliding piston type. The operation and general disposition of the components of this engineannular casing member 2l, rotor 2| l, shaft ZZ,

exchange station grooves 2 3c-d, carrier grooves 214, fuel inlet 223, lubricant injection and pressure channels 224 and 225-ar similar to those described with respect to Fig. 7, with `sliding piston type mobile seals 268, similar to-those of Figs. -14, used in place of roller seals. However, because of the considerable length of the outer block face, the spark plugs 211 are threaded into a radial bore in the casing Opening into the bottom of each of the diametrically opposite exchange station groove 2|3b-2|3d, while outlet ports 221 open through the end plates of the casing. Though onitted from the drawings for the sake of simplicity, it is to be understood that channels may be provided in the rotor shaft and casing members for the circulation of acoolant in the case of internal combustion engines as shown in Figs. 7 and 16.

For high pressure pumps where theforward retaining shoulder against which a stationary seal seats is preferably steeply inclined to increase the sealing pressure, another form of seal retaining formation may be used in the outer casing to aid in the escape of a seal held stationary therein. Fig. 17 shows such a seal retaining formation having a stationary seal lifter in the form of an arcuate rotatable insert 293 rollin in a Semi-circular recess 29| extended across the outer race face. i On at least one end of 298 a cylindrical extension zszco-axial with the recess 295 is journalled in a bore in the casing to allow rotatijon of the lifter. The roller' '295 in Seating in the exchange station bears ;against shoulder 298. When a roller 291 is carried into the exchange station, it bears out- ;wardly against a bearing surface 298 to cause rotation of the lifter in a clockwise direction, thereby lifting the roller 295 slightly to aid its escape over the shoulder 295.

In addition to the free roller and sliding block types of seals hitherto described, other forms may be used which move in the exchange sequence already illustrated. Thus in Figs. 18-20, a casing, comprising the side wall 3l, the side wall 332 with integral cylindrical wall 30 3 held together by bolts 394, encloses a pair of circumferentially fianged disks 385, 381 disposed on either side of rotor disk 368 of which the hub 389, keyed to rotate with shaft 3 i 0, extends into central apertures of the seal disks. The shafi; 3|0 may be Jourrailed and sealedto the casing in any suitable manner.

The offset portion 3|2 of disk 301, from which the annular fiange 3| 3 extends, is accommodated in an annular recess 305'in wall 302. Disk 336 is provided with an annular fiange 3|4 spaced from fiange 3|3 and extendedto the offset 3|2 to enclose the rotor and central portion of disk 301. As fiange 3|3 is provided with at least one inwardly extended sealing block 3|5 afiixed to the fiange and the offset portion, and disposed in slidable sealing relation to fiange 3| l and wall 301, and as fiange 3|4 isprovided with at least one outwardly extended sealing block 3|l in slidable sealing relation to wall 30l, fiange 313 and offset 312, a, plurality of fluid working cham-'- bers of operatively variable size are available fo utilization in a pump, motor or interna combustion engine by incorporation of auxiliary structures as already discussed for previous devices. spring biased sealing bars similar to those on the slding blocks of F'igs. 14 and 14a may be used. However, the number of blocks on one seal disk is equal to those on the other, and where a plurality of blocks are used on a disk they are symmetrically spaced.

To lock the seal bearing disks and hence the corresponding seal blocks relative to rotor or casing, the dlsks are provided with looking devices siii, 325] axially movable in aperture 321, 322 into engagement respectively with casing recesses 323, 324 or with rotor aperture- 32| When more than one seal block is provided on each disk, then a corresponding number of lookin devices and auxiliary' structures must be used. In Figs. 18-19, dsk 38? is locked to the casing by 320 seated in recess 324 and disk 306 is locked to the rotor by 319 and is moved therewith causing seal 3i l to translate in the'annular space toward seal 315. With inlet ports 321 and exhaust port 328 Opening throu h the side wall Bill' on opposite sides of the position where the seal *blocks stop (position of 3i6) and with the mechanism operatin'g as a pump, fluid is drawn in through 321 behind a seal block receding from 316, while fluid is expelled through 328 by advancing block 3I1. The consequent pressure difierencebetween the two sides of the stationary seal block 3|6 tends to move that seal block and hence the disk 301 in the direction of rotor rotation, with the result that the advance slope of recess 324 tends to cam the lock means 329 toward the rotor. When the rotor aperture 325 comes opposite'the disk aper- V ture 322 i. e. the seal carrier and retaining formations are passing or in transit, 320 is allowed to cam into the rotor displacing 3|9 into the recess 323. This exchange action, which is about to begin in Fig. 20, results in the rotor picking up disk 337 released from the casing and in the release'of disk see by the rotor to a stationary relation upon' engag'ement by the casing. In other words, after exchange has taken place the 'conditions shownin Fig. 19 will be reversed, with sealing block iil stationary at the position formerly 'o'ccupied by 326, and with 3|6 advancing.

As shown in the drawings, the looking devices have cylindrical bodies, semi-hemispherical outerends and slightly convex inward base ends with slightly rounded edges.` The length of each looking member should be close to and not exceeding the thicknessof rotor -disk'308 plus the seal bearing 'disk thickness, while the contour of each casing recess must be such, first as to allow Seating of the looking means at a depth permitting the rotor to escape the inward ends of the looking devices, andsecondly, with respect to the 'correspon'ding recess on the opposite plate,"as' to successive individual seals from translation relative to the corresponding member, seal engaging means on one of said members being adapted to cooperate with seal engaging means on the other said member to eect exchange of engaged mobile seals between said members during relative rotation thereof, whereby the chambers between successive mobile seals are continually varied in size.

5. A mechancal action comprising a rotor member and a stationary member in coaxial relation thereto forming an orbital fluid working space, a plurality of mobile sealing means disposed in sealing relation between said members and dividing said space into chambers, seal carrier means associated with said rotor member adapted to positively mechanically engage and move individual sealing means relative to said stationary member, and seal exchange means associated with said stationary member adapted to positively mechanically engage and retain individual sealing means from movement; said carrier, exchange means and sealing means being mutually adapted in form for exchange of moved and retained seals during transit of carrier means relative to exchange means.

6. A device as described in claim 1 wherein a plurality of mobile seal carrier formations is provided on the said rotatable member, the number of mobile seals being equal to the total number of said seal carrier and seal engaging retaining formations.

7. A device as described in claim 1 wherein a plurality of mobile seal retaining formations is provided on the said fixed member, and seal carrier formations exceeding the number of said retaining formations, the number of mobile seals being equal to the total number of said seal carrier and seal retaining formations.

8. A rotary fluid displacement mechanism having a pair of relatively rotatable members comprising a cylindrical central member and a hollow casing member enclosing said central member with an inner cylindrical surface spaced about the cylindrical surface of said central member, said casing member including side walls whereby a closed fluid working space is provided about the periphery of said central member, a plurality of mutually displaceable mobile seals disposed in said space to divide the working space into a plurality of fluid chambers of operatively varying size, a mobile seal carrier formation on the peripheral surface of the rotatable member adapted to positively mechanically engage and translate a mobile seal in sealing relation to said cylindrical surfaces, a mobile seal exchange station formation in the surface of the other member adapted to hold positively and mechanically a mobile seal from translation and in sealing relation to said inner and outer cylindrical surfaces, said formations being contoured to allow simultaneous exchange of seals between the carrier formation and exchange station formation as a carrier formation transits an exchange station, and fluid inlet and exhaust conduits Opening into said space through paired inlet and exhaust ports disposed respectively at either side of said exchange station.

9. A device as described in claim 6 wherein mobile seals are provided in the form of rollers.

10. A device as described in claim 6 wherein each of said formations comprises a groove provided with a seal engaging shoulder; and wherein each said mobile seal comprises a sliding block in the form of an annular sector having there- 13 through a radial aperture and looking means extended the length of said aperture and projecting therefrom, said locking means being radially movable in one direction into engagement with a shoulder of a carrier formation and in the opposite direction into engagement with a shoulder of a seal engaging formation. 7

11. A device as described in claim 2 wherein one of said side wall elements is biased against said central member to provide sealing pressure on the end of said central member.

12. A rotary pump mechanism having a pair of relatively rotatable members comprising a rotor member and a hollow casing member enclosing said rotor member with inner peripheral surface spaced about an outer peripheral surface of said rotor member, said casing member including side walls whereby a closed fluid working space is provided about the circumference of said rotor member, a plurality of mutually displaceable mobile seals disposed in said space to divide the working space into a plurality of fluid chambers of operatively varying size, a mobile seal carrier formation on the peripheral surface of the rotor member adapted to positively mechanically engage and translate a mobile seal in sealing relation to said inner and outer peripheral surfaces, a mobile seal exchange station formation in the peripheral surface of the casing member adapted to positively mechanically restrain a mobile seal from translation and in sealing relation to said inner and outer peripheral surfaces, said formations being contoured relative to each other and to said seals to allow simultaneous exchange of seals between the carrier formation and exchange station formation as a carrier formation transits an exchange station, and fluid inlet and exhaust conduits Opening into said space through paired inlet and exhaust ports disposed respectively at either side of said exchange station.

13. An internal combustion engine having a mechanism as described in claim 2, wherein there is provided an even number of said mobile seal retaining formations and a number of carrier formations at least equal to the number of said seal retaining formations, each said formation having a forward and .a rear seal engaging shoulder; and paired fuel intake and exhaust ports and fuel igniting means in said fixed member alternately .associated with successive seal retaining formations, the paired inlet and outlet ports being disposed respectively toward the rotationwise and anti-rotationwise sides of the mobile seal Seating position of a corresponding seal retaining formation and said igniting means being disposed rotationwise of the rear seal engaging shoulder of a corresponding seal retaining formation.

14. A device as described in claim 1 wherein the seal carrier formations exceed the number of said retaining formations, the number of mobile seals being equal to the total number of said seal carrier and seal retaining formations.

15. A device as described in claim 1 wherein each of said formations comprises a groove provided with a seal engaging shoulder; and wherein each said mobile seal includes a sliding block in the form of an annular sector, said seal having therethrough an aperture and looking means extended the length of said aperture and projecting therefrom, said looking means being mov- .able in one direction into engagement with a shoulder of a carrier formation and in the opposite direction into engagement with a shoulder of a seal retaining formation. 

